Adjusting means for hydraulic governor compensating springs



Oct. 9, 1951 R. w. TAYLOR ADJUSTING MEANS FOR HYDRAULIC GOVERNOR COMPENSATING SPRINGS 4 Sheets-Sheet 1 Filed Oct. 4, 1945 MIXING VALVE FUEL PUMP THROTTLE VALVE OR OTHER ENERGY MEDIUM CONTROL gwuwwbo'o ROBERT W. TAYLOR FIG. I

Oct. 9, 1951 R. w. TAYLOR ADJUSTING MEANS FOR HYDRAULIC GOVERNOR COMPENSATING SPRINGS 4 Sheets-Sheet 2 Filed Oct. 4, 1945 ROBERT W. TAYLOR 1951 R. w. TAYLOR.

ADJUSTING MEANS FOR HYDRAULIC GOVERNOR COMPENSATING SPRINGS 4 Sheets-Sheet 5 Filed Oct. 4, 1945 art/OW ROBERT W. TAYLQR Oct. 9, 1951 R w TAYLOR 2,570,287

ADJUSTING MEANS FOR HYDRAULIC GOVERNOR COMPENSATING SPRINGS Filed Oct. 4, 1945 4 SheetsSheet 4 use 3mm ROBERT w. TAYLOR Patented Oct. 9, 1951 UNITED 'STATES PATENT OFFICE.

ADJUSTING MEANS FOR HYDRAULIC GOV- ERNOR OOMPENSATING SPRINGS 2 Claims.

amended April 30, 1928; 370 O. G. 757) which will operate to eliminate or reduce withinpractical limits hunting of the governed prime mover during load changes. However, means have heretofore been unknown for making fine adjustments of the compensating mechanism embodied in commercial designs without disassem bling the mechanism. This is objectionable in view of the time and skill which is necessitated in making accurate adjustments for close regulation of the prime mover.

An object of the invention is to provide in a governor of the above described character a novel adjusting mechanism which may be pre-set more accurately than speed compensation controls heretofore provided.

Another object is to provide an improved adjusting mechanism for governor hydraulic compensating means which may be operated externally of the governor casing without disassembling the governor mechanism or component parts thereof.

A-further object is to provide an improved adjusting mechanism for controlling the hydraulic compensating means of a governor which may be securely locked in the adjusted position.

The invention also resides in certain novel structural characteristics which facilitate carrying out the foregoing objects and which contribute both to the simplicity of the adjustable governor hydraulic compensating mechanism, and to the reliability of operation as well as to the ease and expeditious manner of making the desired adjustments.

Other objects and advantages of the invention will become apparent from the following detailed description taken in connection with the accompanying drawings, in which:

Figure I is a vertical sectional view through a governor made in accordance with one embodi ment of the invention;

Figure 2 is a horizontal section on line 2-2 of Figure 1;

Figure 3 is an enlarged detailed view taken on line 3-3 of Figure 2 showing the embodiment of the valve compensation spring and means disclosed in Figures 1 and 2;

adjusting a 2 a Figure 4 is a longitudinal sectional drawing through a governor having modified arrangements of parts, and

Figure 5 is an enlarged detailed view showing the valve compensating spring and adjusting means embodied in the governor mechanism shown in Figure 4. While the invention is susceptible of various modifications and alternative constructions; I have shown in the drawings and will herein describe in detail the preferred embodiments. It is to be understood, however, that I do not intend to limit the invention by such disclosure for Iaim to cover all modifications and alternative constructions falling within the spirit and scope of the invention as defined in the appended claims. The drawings show the invention incorporated in a main hydraulic governor In which operates alternately in response to small increases and decreases in the speed of a prime moverinot shown) to adjust the position of a rod ll connected through a mechanical linkage 12 to a fuel pump, gas mixing valve, throttle valve or other device indicated by reference numeral l3 for controlling the supply of an energy medium to maintain the speed of the prime mover substantially constant.

Referring to Figure 1, the governor I0 is formed of a governor body l4 positioned upon a base l5 which may be secured on or adjacent to the prime mover. A spring biased hydraulically actuated servomotor l6 which serves to modulate the speed of the prime mover is supported adjacent to one side of the governor-body I l. The servo- -motor comprises a hollow element ll in which is formed a main cylinder I3 between member 25 and spring cover 23 and an auxiliary cylinder chamber l9 between member 26 and apertured closure plate 24. Secured by nut 25 to one end of rod l I is a main piston 20 located in cylinder chamber I 8. An auxiliary piston 2| is secured intermediate the ends of rod 1 I in cylinder chamber l9. One end of cylinder chamber I8 is closed by the spring cover 23 and one end of cylinder chamber 19 is closed by the aperture closure plate 24 which contains suitable bearing through which rod ll passes. Openings 21 and 28 are provided in hollow element I! for the passage of fluid to and from cylinder chambers l8 and I9, respectively. A compression spring 22 serves to urge the main piston 20 together with the auxiliary piston 2| and rod H in a downward direction. Downward movement of rod H transmitted through linkage l2 actuates the fuel controlling is enclosed a piston 4'! and a compensating spring assembly. A plurality of apertures 31, 38, 39 and 40 extend radially at spaced intervals throughout the length of said rotatable sleeve. Pilot valvebushing 32 is contained within the central opening of the rotatable sleeve 3| and consists of a tubular upper portion 33 and a piston 41 secured to the lower extremity of the tubular portion. Ports 4| and 43 and regulating port 42 are formed at spaced intervals in the tubular portion 33 of valve bushing 32. Extending from said tubular portion 33 is a rod 34 having its end. threaded to receive an adjusting nut 35. An additional element of the valve mechanism comprises a pilot valve plunger 36 adapted for slidable movement within the tubular portion 33 of pilot valve bushing 32. .A plurality of lands 44, 45, and 48 are located at spaced distances between the ends of the pilot valve plunger as shown in Figure 1.

Hydraulic pressure for the operation of the governor parts is supplied by a pump formed of driving spur gear 50 positioned at the lower extremity of longitudinal bore 30 and journaled at 52 in base l5 and a driven spur gear 5|, which is mounted on stub shaft 53 in recess 54 formed in body M. The driving spur gear 50 is hollowed to receive the splined section of drive shaft 55 which extends through base I5 and is fitted with suitable drive members such as bevel gears 56, 51 and shaft 58 which serve to connect shaft 55 for rotation to the prime mover. Base I5 is provided with a suitable bearing and oil retainer which support and maintain the drive shaft 55 in the position shown in Figure 1. An extension 59 of the driving spur gear 50 is connected by screws 60 to rotatable sleeve 3| so that the sleeve and driving spur gear are rotated as a unit by the prime mover.

Ihe upper extremity of the rotatable sleeve 3| is connected to a yoke 6| provided with pivots 62 which serve to support bell cranks 63.. One arm of each of the bell cranks B3 is threaded to receive correspondingly threaded nuts 64 which Serve as the fly balls for the governor. The other arm of each bell crank engages the outer race of ball bearing 65. It will be apparent that rotation of rotatable sleeve 3| will serve to rotate yoke 6| and that fly balls 64 which are free for radial movement by centrifugal force will assume various positions depending upon the speed of the prime mover. Radial movement of the fly balls will cause the bell cranks 63 to rotate about pivots 62 and move bearing 55 either upward or downward in a. vertical direction. Out-ward movement of the fly balls 64 is resisted by speeder spring 65 which has one end seated on a collar 61 and the other end engaging an adjustable abutment 6.8. The position of the abutment 58 maybe manually adjusted by means outside of thegovernor casing (not shown) by rotation'of pinion 59 which engages the rack 10 to move the abutment in its slidable mounts identified by reference numeral 7|. Collar 61 is secured to an. extension 12 of pilot valve plunger 36 which extension i tightly fitted to the inner race of ball bearing 65. Thus the pilot valve plunger may be moved in a vertical direction by the action of the fiy balls, but it will not rotate with the yoke 6|. A cover l3 secured to governor body .|4 is provided toenclose the fiy balls, Speeder spring, and mountings as is shown in Figure l.

. One modification of the compensating spring and adjusting means therefore is best shown in Figures 2 and 3. An upper spring collar 16 is slidably mounted on rod 34 and maintained a spaced distance from piston 41 by spacer 15. A sleeve 11 is secured to the interior of the rotatable sleeve 3| by screw 18 and a portion '19 thereof extends between collar 16 and piston 41. The lower spring collar is cupshaped and the bottom is centrally drilled and tapped to receive the correspondingly threaded shank of flange 8| Compensating spring is positioned between upper spring collar 16 and. lower spring collar 80. Flange 8| is provided with a central opening to slidably receive rod 34 and nut 35 prevents rod 34 from slipping through the flange when pilot valve bushing 32, is raised. As is shown in Figure 3, flange 8| bottoms on ledge 82. The flange is connected to sleeve Tl by pin 83 which projects into a vertical slot 84 formed in sleeve 11. As shown in Figure 2,. the lower spring collar 80 is exteriorly threaded to receive the threadsof a worm which is mounted in chamber 9|. Chamber 9| extends tangentially into the sleeve H and rotatable sleeve 3|. Worm 99 is provided with a shank 92 which is fitted for rotation in extension 93 of chamber 9|. On the end of the worm opposite the shankvfiz, a socket 94 is provided which constitutes a female coupling element for the worm. A set screw 95 having a central bore is positioned in an enlarged threaded extension of chamber 9| and is adapted to be tightened against worm 90 to secure it in an adjusted position. In addition to the central bore, set screw 95 is provided with castellations 96 which serve as a female coupling connection. It will be noted from Figure 2 that the threads of worm 90 are in engagement with the exterior threads of the lower spring collar 8!] and that the assembly of set screw 95, worm 90, lower spring collar 80, sleeve l1 and rotatable sleeve 3| are rotated in unison by the prime mover.

Manual means for adjusting the vertical position of lower. spring collar .80 and hence the compression of compensating spring 85 and also for securing the adjustment of the collar from outside of the casing are indicated by reference numeral I00 in Figure 2. bored at HH and I02 and drilled and tapped at I03 to engage the external threads. of bushing M which extends through the outer wall of the governor body. P0sitioned within the'bushing and extending from the exterior into the interior of the governor body l4 are worm operatingshaft I05 and set screw operating shaft I06 which are concentrally located and arranged for sliding movement. Set screw operating screw shaft I06 comprises a tubular member provided at the outer end with a handle H3 and at the inner end with a male coupling means 108 adapted to engage the castellated coupling of set screw 95.

.Shaft I06 is slidably mounted in bushing I04 and Governor body I4 is.

betrween bushing I04 and slidable shaft I06 is provided by a gland IIO which maintains pack- .ing material II I in place between shaft I06 and bushing I04. Worm operating shaft I which is slidably mounted within shaft I06 is provided at its outer end with handle I01 and at its inner extremity with male coupling element II4 which is adapted to engage with socket 94 of worm 90. Compression spring II5 serves to urge shaft I05 out of engagement with worm 90 and the engagement of collar IIB with handle II3 limits the outward movement of the shaft. Cover II! which is internally threaded at its open end to engage externally located threads on bushing I04 is positioned over handles I 07 and H3 to pre- .v ent accidental sliding of the corresponding shaft inwardly during operation of the governor.

The mechanism above described enables the position of the lower spring collar 80 to be varied in a vertical direction from Without the governor casing which in turn will serve to pre-set the tension of compensating spring 85. When it is desired to make an adjustment, rotatable sleeve 3| is positioned with chamber 9| in axial alignment with coupling elements H4 and I08 on shafts I05 and I06 respectively. This can readily be done by removing inspection plate H8 and aligning the yoke 6| with an appropriate mark ,on thegovernor body. Cover II'I is-removed to expose the operating handles 3 and I 01 and shaft I06 is pushed inwardlyagainst the action of spring fitw untilthe male coupling means I08 engages the female coupling means of set screw 95. The set screw 95 and shaft I06 are rotated by. handle ;II3 in a direction to back-off th set screw thus unlocking worm 90. ShaftI05ais then moved inwardly until the male coupling means 114 engages socket 94 of worm 90. With the partsin this position, 'the worm may be turned by handle I01 which in turn causes the lower spring collar 80 to rotate on the threads of fiaiige 8|. In this manner the spring collar may beraised or lowered to pre-set the tension of spring 85. After the desired adjustment has been made,.coupling means H4 and 94are disengaged and shaft I05 returned to the position shown inFigure 2 by the action of spring H5. Shaft. I06 ispressed inwardly so that coupling nji'ansWBB. and 96 are in engagement and the set'screw 95 is rotated by handle I I3.to.lock worm 95 in its adjusted position after which handle ll3. is'.released and spring I09 serves to return .it to the position shown in Figure 2.

i The intake to spur gear pump 50-5I communicates with a sump identified by reference r numeral I I28 in which on or other hydraulic fluid is contained. ,.The hydraulicfluid is inserted through'filler opening 99 and flows to the sump through passages (not shown). The discharge side of the pump communicates with the storage chamber of accumulators I2I provided with pistons: I22 which'arebiased by springs. II9 whereby a relatively constant oil pressure is maintained. A by-pass (not shown) is employed in a known manner from the discharge side of gear pump 50-5I'to'the sump for relieving excess oil pressure. 1 fjH'Whe'n the prime mover is rotated at normal speed u'n'der steady load, the fiyballs 64, pilot valve plunger 35 and pilot valve bushing 32 are in norinal positions with respect to the regulating port 42in the pilot valve plunger as shown in Fig- 'ure 1.. i Upon decrease of load upon the prime mover, its speed increases and the fiyballs 64 are moved 6 outwardly by centrifugal force. Outward movement of the fiyballs causes the pilot valve plunger 36 to be raised whereby land 45 uncovers regulating port 42 in the pilot valve bushing 32. This completes an open oil passage from main cylinder chamber I8 to the'sump through opening 21, duct I23, aperture 38, regulating port 42, and port 43 and the compression spring 22 serves to move the main piston 20 downwardly which results in the downward movement of rod II which actuates the fuel supply control I3 through linkages I 2 to decrease the fuel supply to the rime mover. As the main piston 20 and rod II move downwardly, auxiliary piston 2I also moves downward- 1y, drawing oil into auxiliary piston chamber I9 from above pivot valve bushing piston 41 through opening 28, duct I 24 and aperture 40 resulting in the upward movement of pilot valve bushing 32 and the expansion of spring 85. This movement continues until the regulating port 42 is covered by land 45 at which point the main piston 20 and rod II are stopped in a position corresponding to the decreased amount of fuel necessary to operate the prime mover at normal speed under the decreased load. As the speed decreases to normal, fiyballs 64 move radially inward to normal position due to the decreased centrifugal force, causing the pilot valve plunger 36 to be lowered to normal position. The compensating spring acts to return the pilot valve bushing 32 to normal position at the rate the pilot valve plunger moves thus keeping the regulating port 42 covered by land 45 and the main piston 20 stationary. The rate of movement is controlled by the pre-set compression of spring 85 and rate of oil flow through needle valves I25. At the completion of the cycle above described, the fiyballs 64, pilot valve plunger 36 and pilot valve bushing 32 are in normal positions and the main piston 20 is stationary at a position corresponding to the decreased amount of fuel needed to operate the prime mover at normal speed under the decreased load.

Upon increase of load on the prime mover, its speed decreases and fiyballs 54 move radially inward by lowering pilot valve plunger 35 which causes regulating port 42 to be uncoveredby land 45. This completes an open passage between the oil under pressure in the accumulator, I2I to main cylinder chamber I8 thru aperture 31, port 4|, regulating port 42, aperture 38, duct I23 and opening 2'! resulting in the upward movement of main piston 20 and red I I against the pressure of spring 22 and actuation of the fuel supply control I3 through linkages I2 to increase the fuel supply to the prime mover. Upward movement of rod I I causes upward movement of auxiliary piston 2| which serves to force oil from auxiliary piston chamber I9 into piston chamber 48 through opening 28, duct I24 and aperture 40 resulting in the downward movement of pilot valve bushing piston 4'! and the compression of spring 85. The downward movement of pilot valve bushing piston 41 continues until the regulating port 42 is covered by land 45 on the pilot valve plunger 36 at which time the main piston 20 is stopped at a position corresponding to the increased fuel needed to operate the prime mover at normal speed under increased load. As the speed increases to normal, fiyballs 64 return to normal position raising the pilot valve plunger 36 to normal position. The pilot valve bushing 32 is returned to normal position by the action of the compensating spring 05 at the same rate as the il ra s a tain hvek p a gee l'a-ting port IZv covered by land 45 and the main piston stationary. The speed of return of the pilot valve bushing is dependent upon the adjustment of the needle valves I and the adjustment of the compensating spring. At the completion of the cycle above described the flybeen rearranged andredesigned so that the pre- 1 set compression of compensating spring I3IZI may be manually adjusted from outside of the governor' body I 3I while the prime mover and the governor are in operation. In this modification,

yoke I32, pivoted bell cranks I33 and flyballs I34 are adapted to be rotated in bearing I41 by shaft I35 which is connected to the prime mover (not shown). Shaft I35 is connected to driving spur gear I36 which meshes with driven spur gear I31, both constituting a pump for supplying oil pressure to the governor. Gear I40 attached to yoke I32' is driven by the driven spur gear I31 through shaft I38' and gear I39. The inner extremities MI of bell crank arms I33 are pivotally connected to extension I42 of pilot valve bushing I53 which is connected to the inner race of ball bearingI4'4. Speeder spring I45 is mounted between the outer race of ball bearing I44 and the manually adjustable abutment I46. As will be noted in Figure 4, the speeder spring tends to bias the flyballs I34 inwardly. Pilot valve bushing I43 is provided with port I48 and regulating port Ids which cooperate with chambers in the governor body I3I, and is recessed at the bottom to receive the pilot valve plunger I50. In this modification, pilot valve plunger I5!) is provided with land I5I and also land I52 which normally covers regulating port I49. The lunger is attached at I53 to the lower extremity of pivot valve plunger piston-I54 located in compensating spring chamber I55. The top of compensating spring I39 presses against the bottom side of piston I54 and the spring bottoms on adjustable spring collar I56 which is cut-shaped and provided with threads I51 on the periphery thereof. drilled and tapped at I58 to receive the threaded shank I59 of flange I60 which is secured against rotation in the lower part of cylinder chamber I55. The threads I51 on the outer periphery of spring collar I56 are engaged by worm gear IGi which is manually rotated by shaft I62. Shaft I62 extends outside of the governor bod and is provided with an operating handle (not shown).

Rotation of worm gear I6I serves to rotaLe spring collar I56 on the threaded shank I59 which re- 'sults in movement of the collar in a vertical direction in order that the compression of compensating spring I30 may be adjusted.

The servo-motor identified by reference numeral I65 comprises a casing I56 secured adjacent to governor body IN. The casing is recessed and partitioned at lit to provide cylinder chambers I51 and I68. Piston I69 is located within the recess and has operating faces HI and I12 located in cylinder chamber I51 and IE8, respectively. The piston I69 is secured to shaft I13 which is connected at its upper end to compression spring I14 and at its lower end through mechanical linkage to the mixing valve, fuel pump, throttle valve or'other device (notshown) The bottom is 8 for controlling the supply of an energy medium to the prime mover. A duct I15 extends between cylinder chamber I61 and regulating port I49 and duct I16 extends between cylinder chamber I68 and cylinder chamber I55 in which thepil'ot valve plunger piston is located. A needle" valve represented by reference numeral I11 is provided in order to relieve the oil pressure existing therein to sump I18. The operation of the'modified governor to maintain constant speed'of the prime mover upon either increase or decrease orioa-dis substantially the same as the operation above set forth except that in this modification, the radial movement of the flyballs I34 serves to move the pilot valve bushing I43 and the compensating action of spring I 35 is applied through pilot valve plunger I50. 1

From the above description it will be apparent that the compensating spring of thegovernor can be accurately pre-set to prevent hunting. and to obtain close regulation of the prime mover without disassembling of the governor. The acjustment of the compensating spring canconvenientl be made by manipulation of the externally positioned controls and after the adjustment is made, the mechanism can be secured in the adjusted position in order to maintain the regulating action of the governor.

The invention described herein may be made or used by or for the Government of the United States for governmental purposes without the payment to me of any royalties thereon or therefor. I Iclaim: v

1. In a hydraulic speed responsive governor of a type having a liquid valve means for controlling the speed of a prime mover, an adjustable compensating spring for eliminating surging and hunting of the prime mover and adapted tobear at its upper end against a movable member, means for manually adjusting the precomprese sion of said compensating spring, said manually adjusting means comprising a cup shaped collar for supporting the lower end of said spring, a

worm gear mounted on the outer side of said collar, a worm mounted adjacent said collar and adapted to engage said worm gear, said worm,

worm gear and collar being constructed and arranged to enact the adjustment of said spring upon the rotation of said gear and collar; by said worm, means for locking said spring in its adjusted position, said adjusting and locking means further comprising a tubular shaft extending transversely of said collar and in axial alignment with said worm, a second shaft concentrically mounted within said tubular shaft, said tubular shaft having means on one end thereof adjacent said collar for unlocking said collar, said second shaft having means on one end thereof adjacent said collar for adjusting said vcollar, means normally maintaining said shafts,

out of engagement with said collar, handle means spring, indentations imposed on the outer" side of said collar, adjustable means positioned adjacent to and in contact with the indentations on said collar so that movement of said adjustable means imparts reciprocating movement to said collar and consequent alteration of said spring, means for locking said collar in its adjusted position, said adjusting means and locking means further comprising a tubular shaft in axial alignment with said adjustable means, a second shaft concentrically mounted within said tubular shaft, said tubular shaft having means on one end thereof adjacent said collar for unlocking said collar, said second shaft having means on one end thereof adjacent said collar for engaging said adjustable means, and handle means located on the opposite ends of said shafts to facilitate turning of said shafts to a desired position.

ROBERT W. TAYLOR.

10 REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,020,326 Pearson Nov. 12, 1935 2,073,426 Pearson Mar. 9, 1937 2,117,891 Kalin May 17, 1938 2,144,429 Martin Jan. 17, 1939 2,179,696 Keel Nov. 14, 1939 2,273,408 Woodward Feb. 17, 1942 2,364,116 Whitehead Dec. 5, 1944 2,371,793 Bourland et al Mar. 20, 1945 2,374,083 Drake Apr. 17, 1945 2,390,144 Gossling Dec. 4, 945

FOREIGN PATENTS Number Country Date 4,750 Great Britain Mar. 6, 1890 

